EP3126651A1 - Flap device for an internal combustion engine - Google Patents

Flap device for an internal combustion engine

Info

Publication number
EP3126651A1
EP3126651A1 EP15707573.0A EP15707573A EP3126651A1 EP 3126651 A1 EP3126651 A1 EP 3126651A1 EP 15707573 A EP15707573 A EP 15707573A EP 3126651 A1 EP3126651 A1 EP 3126651A1
Authority
EP
European Patent Office
Prior art keywords
bearing
shaft
bore
flow channel
internal combustion
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP15707573.0A
Other languages
German (de)
French (fr)
Other versions
EP3126651B1 (en
Inventor
Hans Gerards
Andreas GRAUTEN
Jürgen Michels
Tim Holler
Kirill Klass
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Pierburg GmbH
Original Assignee
Pierburg GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Pierburg GmbH filed Critical Pierburg GmbH
Publication of EP3126651A1 publication Critical patent/EP3126651A1/en
Application granted granted Critical
Publication of EP3126651B1 publication Critical patent/EP3126651B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D9/00—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits
    • F02D9/04—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits concerning exhaust conduits
    • F02D9/06—Exhaust brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D9/00—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits
    • F02D9/08—Throttle valves specially adapted therefor; Arrangements of such valves in conduits
    • F02D9/10—Throttle valves specially adapted therefor; Arrangements of such valves in conduits having pivotally-mounted flaps
    • F02D9/1005—Details of the flap
    • F02D9/101—Special flap shapes, ribs, bores or the like
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D9/00—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits
    • F02D9/08—Throttle valves specially adapted therefor; Arrangements of such valves in conduits
    • F02D9/10—Throttle valves specially adapted therefor; Arrangements of such valves in conduits having pivotally-mounted flaps
    • F02D9/1035—Details of the valve housing
    • F02D9/106—Sealing of the valve shaft in the housing, e.g. details of the bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/52—Systems for actuating EGR valves
    • F02M26/53—Systems for actuating EGR valves using electric actuators, e.g. solenoids
    • F02M26/54—Rotary actuators, e.g. step motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/16—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members
    • F16K1/18—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps
    • F16K1/22—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps with axis of rotation crossing the valve member, e.g. butterfly valves
    • F16K1/224—Details of bearings for the axis of rotation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/16—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members
    • F16K1/18—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps
    • F16K1/22—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps with axis of rotation crossing the valve member, e.g. butterfly valves
    • F16K1/226—Shaping or arrangements of the sealing
    • F16K1/2268—Sealing means for the axis of rotation

Definitions

  • the invention relates to a flap device for an internal combustion engine having a flow housing defining a flow channel, a flap body which is rotatably disposed in the flow channel, a cantilevered shaft on which the flap body is mounted, a first bearing which is arranged in a first bearing receptacle and radially surrounding the shaft, an actuator, via which the shaft and the flap body are rotatable in the flow channel, an actuator housing in which the actuator is arranged and a bore, which opens from a space surrounding the shaft in the flow channel.
  • flap devices are used, for example, as exhaust gas flaps or exhaust gas recirculation valves in low-pressure or high-pressure exhaust gas circuits or as throttle valves in the intake tract of internal combustion engines and serve to control an amount of exhaust gas attributable to the cylinders or to regulate the pressure in the exhaust gas recirculation channel to reduce pollutant emissions of the engine or to control the intake air quantity ,
  • EP 1 426 589 A2 proposes a single-sided flap device in which a space is formed in the housing in the flow direction in front of the bearing, via a bore with the flow channel on the downstream side the flap is connected. In this embodiment, however, the bearing is not protected against ice formation in the parked state of the internal combustion engine.
  • EP 2 372 136 A2 a two-way mounted exhaust flap is known, the side facing away from the actuator is mounted in a closed plastic bush, in which a recess is formed, which is connected via a bore in the flow housing with the flow channel to the Shaft to protect against ice formation or other deposits.
  • a design is not suitable due to the recess in the camp itself for thermally highly resilient carbon graphite bearings.
  • the actuator side facing such an embodiment is not provided, since this would lead to a thermal overload of the actuator.
  • the shaft protrudes into the actuator housing and is mounted on one side via the first bearing and a second bearing, wherein the first bearing receptacle is formed on the flow housing and the space from which the bore opens into the flow channel, between the first and the second Storage is arranged, condensate, which along the shaft reaches the back of the first bearing, can be reliably guided back into the flow channel.
  • a freezing of the shaft after stopping the engine is reliably prevented, so that damage to the bearing, which is usually designed as a carbon graphite bearing can be prevented.
  • the bearing which is usually designed as a carbon graphite bearing
  • the bore is formed in the first bearing receiver, which is formed on the flow housing, so that the bearing itself does not have to be processed and can be performed as a complete hollow cylinder.
  • the bore is formed in the first bearing. A corresponding flattening on a carbon bush can be introduced directly in the compact.
  • a shoulder-shaped enlargement is formed at the axial end of the first bearing on the side opposite the flow channel side of the bearing receiver and extends the bore parallel to the shaft of the heel-shaped extension of the flow channel. Accordingly, the bore can be performed as a simple longitudinal bore. The arrangement of the paragraph at the end At the same time, the first bearing ensures that there is no liquid inside the bearing seat, which bears axially against the bearing.
  • the bore is formed in the installed state of the flap device in the geodetically underlying area of the bearing receptacle. This means that due to gravity existing liquids always get to the hole even in small quantities, since this is formed at the lowest point of the bearing support.
  • the bore in the flow passage closing position of the flap body is preferably arranged on the downstream side of the flap body.
  • the second bearing is arranged at a distance from the first bearing in a bearing receptacle of the actuator housing. This ensures a reliable, easily rotatable bearing of the shaft.
  • the space for receiving the condensate water thus forms between the two housings, whereby the production of the bore is significantly simplified.
  • the flow channel runs horizontally and the bore is arranged in a plane which is defined by a vector which is perpendicular to the central axis of the flow channel and a vector which runs along the shaft axis. is stretched.
  • the bore can also be arranged at horizontally extending flow channel at the lowest point, whereby the runoff of the water and impurities is ensured.
  • the flap body is of such spherical shape that the bore can be freely flowed through in all positions of the flap body and is arranged in the closed state on its downstream side.
  • the free flow of the bore allows at partial load, the use of the pressure difference at the back of the closed valve body compared to the space between the two camps, while at full load due to lack of pressure differences not with the ingress of liquids or hot blow-by gases in the room is calculated.
  • Figure 1 shows a side view of a flap device according to the invention in a sectional view.
  • Figure 2 shows a perspective view of a flow channel of the flap device according to the figure 1, which is shown cut at the level of the shaft.
  • the flap device according to the invention has a flow housing 10 which delimits a flow channel 12.
  • a flap body 14 is arranged, via which the flow cross-section of the flow channel 12 can be controlled by the flap body 14 is rotated in the flow channel 12.
  • the flap body 14 is mounted on a shaft 16 which projects through the flow housing 10 into the flow channel 12.
  • a driven gear 18 is mounted on the shaft 16, which is part of a transmission 20 designed as a spur gear.
  • This transmission 20 is driven by an electric motor 22 with appropriate energization of the electric motor 22.
  • a drive pinion 26 is mounted on an output shaft 24 of the electric motor 22, which acts as a drive member of the transmission 20, so that the rotational movement of the electric motor 22 is transmitted via the gear 20 geared to the shaft 16 and thus to the valve body 14.
  • the electric motor 22 and the gear 20 thus serve as an actuator 28 of the flap device and are arranged in a common actuator housing 30, which consists of a main housing part 32, in which the electric motor 22 and the gear 20 are mounted and an actuator interior 34 occlusive cover 36, which is fastened with the interposition of a seal 38 on the main housing part 32.
  • the electric motor 22 arranged parallel to the shaft 16 projects parallel to the shaft 16 in the direction of the flow housing 10.
  • a bearing receptacle 40 in the form of a hollow cylindrical projection 42 is formed, which extends in the direction of a hollow cylindrical receiving element 44 on the actuator housing 30.
  • this hollow cylindrical receiving element 44 forms a radially limited receiving opening 46, in which the hollow cylindrical projection 42 of the flow housing 10 projects, wherein the inner diameter of the receiving opening 46 substantially corresponds to the outer diameter of the receiving element 44.
  • first bearing seat 40 of the flow housing 10 designed as a plain bearing first bearing 58 is arranged for the shaft 16, which is made of carbon-graphite and axially abuts against the shaft passage opening radially bounding wall 57.
  • the shaft 16 extends through the first bearing 58 and beyond the projection 52 projecting into the actuator interior 34 into the actuator interior 34.
  • the second bearing receiver 56 has a cross-sectional constriction, at the opposite ends of which a shoulder 60, 62 is formed.
  • the projections 42, 52, the receiving element 44 and the bearings have a common center axis 63, which is also the shaft axis.
  • a second bearing 64 is arranged, which is also designed as a carbon graphite sliding bearing, so that the shaft 16 is mounted twice on a flap side.
  • the valve body 14 facing axial end of this bearing 64 protrudes slightly beyond the heel 54 addition.
  • a thrust washer 66 fixedly arranged on the shaft 16 is pressed against the second bearing 64 via a rotary and compression spring 68 for axial positional fixing of the shaft 16.
  • This rotary compression spring 68 is arranged in the actuator interior 34, the projection 52 radially surrounding and presses against the fixedly arranged on the shaft 16 driven gear 18, so that with this, the shaft 16 is loaded in this axial direction. Furthermore, the two end legs of the spring 68 engage in a known manner so behind behind in Figure 1 unrecognizable projections on the actuator housing 30 and the output gear 18 that the shaft 16 is biased in one direction at least during rotation from the rest position. Accordingly, the shaft 16 is rotated due to the spring force in case of failure of the electric motor 22 in a Notlaufposition.
  • the shaft 16 is surrounded by a sealing ring 70, which abuts axially against the shoulder 62 and seals the shaft passage through the bearing receptacle 56 in the direction of the actuator interior 34.
  • the flow channel 10 is flowed through by exhaust gas.
  • This exhaust gas includes Water and other impurities. Both penetrate through the pulsations in the exhaust line along the shaft 16 in a space 74 between the two bearings 58, 64 and can condense there in particular after switching off the internal combustion engine. At temperatures below 0 ° C, this leads to ice formation in the area of the bearing 58, which in turn can lead to damage to the bearing 58 or sticking of the shaft 16.
  • a bore 76 is formed on the hollow cylindrical projection 42 which extends from the space 74 into the flow channel 12 and extends parallel to the shaft 16.
  • the bearing receptacle 40 widens in the form of a shoulder-shaped enlargement 78 in the direction of the actuator housing 30.
  • This shoulder-shaped enlargement 78 is formed at the level of an axial end 82 of the first bearing 58, so that there is no water inside the protrusion 42 may be located on the bearing 58, when the installation of the flap device in the exhaust line of the internal combustion engine is such that the beginning of this bore 76 is disposed at the geodetically lowest position of the space 74 and the bore 76 steadily drops in the direction of the flow channel 12, so that condensation from the space 74 always flows in the direction of the bore 76 and through it in the direction of the flow channel 12 due to gravity.
  • the bore 76 is located on the downstream side of the valve body 14 in the closed state of the valve body 14, since at this part in operation at part load, ie closed valve body 14 creates a negative pressure, which creates a suction against the space 74.
  • the bore 76 is arranged in a plane which is spanned by a vector which is perpendicular to the central axis of the flow channel 12 and a vector which is along the shaft axis.
  • the door body 14 is spherically shaped to have a bulge 80 arranged such that the outer periphery of the door body 14 is inclined to the upstream side.
  • the flap body 14 At full load, the flap body 14 is in its position opening the flow channel 12, in which, however, only small pressure differences occur, so that the entry of exhaust gas along the shaft 16 in the space 74 is only low and high exhaust gas temperatures are present, which is a condensation of the water prevent in the exhaust.
  • the scope of the present invention is not limited to the embodiment described.
  • the structural design of the housing, the drives or gearbox used as well as the channel and flap shapes are modified.
  • different bearings and seals can be used.
  • the hole can be formed depending on the design of the bearing on the camp itself.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Control Of Throttle Valves Provided In The Intake System Or In The Exhaust System (AREA)
  • Lift Valve (AREA)

Abstract

Flap devices for internal combustion engines having a flow housing (10) which delimits a flow duct (12), a flap body (14) which is arranged rotatably in the flow duct (12), a shaft (16) which is mounted on one side and on which the flap body (14) is fastened, a first bearing (58) which is arranged in a first bearing seat (40) and surrounds the shaft (16) radially, an actuator (28), via which the shaft (16) and the flap body (14) can be rotated in the flow duct (12), an actuator housing (30), in which the actuator (28) is arranged, and a bore (76) which opens into the flow duct (12) from a chamber (74) which surrounds the shaft (16), are known. In order to ensure that no damage of the bearings or the actuator occur as a result of ice formation and no exhaust gas can penetrate into the interior of the actuator, it is proposed according to the invention that the shaft (16) protrudes into the actuator housing (30) and is mounted on one side via the first bearing (58) and a second bearing (64), wherein the first bearing seat (40) is configured on the flow housing (10), and the chamber (74), from which the bore (76) opens into the flow duct (12), is arranged between the first bearing (58) and the second bearing (64).

Description

B E S C H R E I B U N G  DESCRIPTION
Klappenvorrichtung für eine Verbrennungskraftmaschine Valve device for an internal combustion engine
Die Erfindung betrifft eine Klappenvorrichtung für eine Verbrennungskraftmaschine mit einem Strömungsgehäuse, das einen Strömungskanal begrenzt, einem Klappenkörper, der drehbar im Strömungskanal angeordnet ist, einer einseitig gelagerten Welle, auf der der Klappenkörper befestigt ist, einem ersten Lager, das in einer ersten Lageraufnahme angeordnet ist und die Welle radial umgibt, einem Aktor, über den die Welle und der Klappenkörper im Strömungskanal drehbar sind, einem Aktorgehäuse, in dem der Aktor angeordnet ist und einer Bohrung, die von einem die Welle umgebenden Raum in den Strömungskanal mündet. The invention relates to a flap device for an internal combustion engine having a flow housing defining a flow channel, a flap body which is rotatably disposed in the flow channel, a cantilevered shaft on which the flap body is mounted, a first bearing which is arranged in a first bearing receptacle and radially surrounding the shaft, an actuator, via which the shaft and the flap body are rotatable in the flow channel, an actuator housing in which the actuator is arranged and a bore, which opens from a space surrounding the shaft in the flow channel.
Derartige Klappenvorrichtungen werden beispielsweise als Abgasstauklappen oder Abgasrückführventile in Niederdruck- oder Hochdruckabgaskreisläufen oder als Drosselklappen im Ansaugtrakt von Verbrennungsmotoren eingesetzt und dienen zur Regelung einer zu den Zylindern zurückzuführenden Abgasmenge oder zur Regelung des Drucks im Abgasrückführkanal zur Verringerung des Schadstoffemissionen des Motors oder zur Regelung der angesaugten Luftmenge. Such flap devices are used, for example, as exhaust gas flaps or exhaust gas recirculation valves in low-pressure or high-pressure exhaust gas circuits or as throttle valves in the intake tract of internal combustion engines and serve to control an amount of exhaust gas attributable to the cylinders or to regulate the pressure in the exhaust gas recirculation channel to reduce pollutant emissions of the engine or to control the intake air quantity ,
Je nach Einbauort sind diese Ventile sowohl bezüglich der anfallenden Schadstoffmenge als auch bezüglich der herrschenden Temperaturen unterschiedlich stark belastet. Insbesondere bei Ventilen, welche im Abgasbereich angeordnet sind, entstehen einerseits hohe thermische Belastungen der Aktoren und der Lager und andererseits durch im Abgas vorhandene Verunreinigungen die Gefahr eines Klemmens oder einer Schädigung der Lager. Um solche Schäden durch Ablagerungen auf der Welle zu vermeiden, wird in der EP 1 426 589 A2 eine einseitig gelagerte Klappenvorrichtung vorgeschlagen, bei der im Gehäuse in Strömungsrichtung vor dem Lager ein Raum ausgebildet ist, der über eine Bohrung mit dem Strömungskanal an der stromabwärtigen Seite der Klappe verbunden ist. In dieser Ausführung wird jedoch das Lager nicht vor Eisbildung im abgestellten Zustand des Verbrennungsmotors geschützt. Depending on the installation location, these valves are subject to varying degrees of load, both with regard to the amount of pollutants produced and with regard to the prevailing temperatures. Particularly in the case of valves which are arranged in the exhaust area, on the one hand high thermal loads on the actuators and the bearings and, on the other hand, impurities present in the exhaust gas create the risk of jamming or damage to the bearings. In order to avoid such damage due to deposits on the shaft, EP 1 426 589 A2 proposes a single-sided flap device in which a space is formed in the housing in the flow direction in front of the bearing, via a bore with the flow channel on the downstream side the flap is connected. In this embodiment, however, the bearing is not protected against ice formation in the parked state of the internal combustion engine.
Des Weiteren ist aus der EP 2 372 136 A2 eine zweiseitig gelagerte Abgasklappe bekannt, deren vom Aktor abgewandte Seite in einer geschlossenen Kunststoff buchse gelagert ist, in der eine Ausnehmung ausgebildet ist, die über eine Bohrung im Strömungsgehäuse mit dem Strömungskanal verbunden ist, um die Welle gegen Eisbildung oder sonstige Ablagerungen zu schützen. Eine solche Ausführung eignet sich jedoch aufgrund der Ausnehmung im Lager selbst nicht für thermisch hoch belastbare Kohle-Graphitlager. An der entgegengesetzten, dem Aktor zugewandten Seite ist eine solche Ausführung nicht vorgesehen, da dies zu einer thermischen Überlastung des Aktors führen würde. Furthermore, from EP 2 372 136 A2 a two-way mounted exhaust flap is known, the side facing away from the actuator is mounted in a closed plastic bush, in which a recess is formed, which is connected via a bore in the flow housing with the flow channel to the Shaft to protect against ice formation or other deposits. However, such a design is not suitable due to the recess in the camp itself for thermally highly resilient carbon graphite bearings. At the opposite, the actuator side facing such an embodiment is not provided, since this would lead to a thermal overload of the actuator.
Entsprechend bestehen bei den bekannten Ausführungen die Nachteile, dass ein sicherer Schutz gegen Schäden durch Eisbildung bei gleichzeitgier thermischer Belastbarkeit für eine Klappenvorrichtung mit in das Aktorgehäuse ragender Welle nicht gegeben ist. Accordingly, there are in the known embodiments, the disadvantages that a reliable protection against damage due to ice formation at the same time thermal load capacity for a flap device with projecting into the actuator housing shaft is not given.
Es stellt sich daher die Aufgabe, eine Klappenvorrichtung für eine Verbrennungskraftmaschine zur Verfügung zu stellen, bei der eine Funktionssicherheit sowohl bei hoher thermischer Belastung als auch bei Temperaturen der Umgebung unter dem Gefrierpunkt gegeben ist. Insbesondere soll der Aktor vor Überhitzung durch eindringendes Abgas geschützt werden und Schäden an den Lagern durch Eisbildung im abgestellten Zustand des Verbrennungsmotors vermieden werden. Diese Aufgabe wird durch eine Klappenvorrichtung mit den Merkmalen des Hauptanspruchs 1 gelöst. It is therefore the object to provide a flap device for an internal combustion engine, in which a functional reliability is given both at high thermal stress and at temperatures of the environment below freezing. In particular, the actuator should be protected from overheating by penetrating exhaust gas and damage to the bearings by ice formation in the parked state of the engine can be avoided. This object is achieved by a flap device with the features of the main claim 1.
Dadurch, dass die Welle in das Aktorgehäuse ragt und über das erste Lager und ein zweites Lager einseitig gelagert ist, wobei die erste Lageraufnahme am Strömungsgehäuse ausgebildet ist und der Raum, von dem aus die Bohrung in den Strömungskanal mündet, zwischen dem ersten und dem zweiten Lager angeordnet ist, kann Kondensat, welches entlang der Welle auf die Rückseite des ersten Lagers gelangt, zuverlässig zurück in den Strömungskanal geführt werden. So wird ein Festfrieren der Welle nach dem Abstellen des Motors zuverlässig verhindert, so dass Schäden am Lager, welches üblicherweise als Kohle- Graphitlager ausgeführt ist, verhindert werden. Durch den Raum wird ein Eindringen weiter in den Aktor beziehungsweise zum zweiten Lager ebenfalls verhindert, da ein Druckgefälle zwischen dem Innern des Aktors und dem Raum vermieden wird. Bei angestelltem Verbrennungsmotor werden in den Raum eindringende heiße Abgase in den Strömungskanal zurückgeführt. Characterized in that the shaft protrudes into the actuator housing and is mounted on one side via the first bearing and a second bearing, wherein the first bearing receptacle is formed on the flow housing and the space from which the bore opens into the flow channel, between the first and the second Storage is arranged, condensate, which along the shaft reaches the back of the first bearing, can be reliably guided back into the flow channel. Thus, a freezing of the shaft after stopping the engine is reliably prevented, so that damage to the bearing, which is usually designed as a carbon graphite bearing can be prevented. Through the room penetration into the actuator or the second bearing is also prevented, since a pressure gradient between the interior of the actuator and the space is avoided. When the internal combustion engine is in the room penetrating hot exhaust gases are returned to the flow channel.
Vorzugsweise ist die Bohrung in der ersten Lageraufnahme ausgebildet, welche am Strömungsgehäuse ausgebildet ist, so dass das Lager selbst nicht bearbeitet werden muss und als vollständiger Hohlzylinder ausgeführt werden kann. Alternativ ist die Bohrung im ersten Lager ausgebildet. Eine entsprechende Abflachung an einer Kohlebuchse kann direkt im Pressling eingebracht werden. Preferably, the bore is formed in the first bearing receiver, which is formed on the flow housing, so that the bearing itself does not have to be processed and can be performed as a complete hollow cylinder. Alternatively, the bore is formed in the first bearing. A corresponding flattening on a carbon bush can be introduced directly in the compact.
In einer vorteilhaften Ausführung ist am axialen Ende des ersten Lagers an der zum Strömungskanal entgegengesetzten Seite der Lageraufnahme eine absatzförmige Erweiterung ausgebildet und erstreckt die Bohrung sich parallel zur Welle von der absatzförmigen Erweiterung aus in den Strömungskanal. Entsprechend kann die Bohrung als einfache Längsbohrung ausgeführt werden. Die Anordnung des Absatzes am Ende des ersten Lagers stellt gleichzeitig sicher, dass sich keine Flüssigkeit innerhalb der Lageraufnahme befindet, die axial am Lager anliegt. In an advantageous embodiment, a shoulder-shaped enlargement is formed at the axial end of the first bearing on the side opposite the flow channel side of the bearing receiver and extends the bore parallel to the shaft of the heel-shaped extension of the flow channel. Accordingly, the bore can be performed as a simple longitudinal bore. The arrangement of the paragraph at the end At the same time, the first bearing ensures that there is no liquid inside the bearing seat, which bears axially against the bearing.
Besonders vorteilhaft ist es, wenn die Bohrung im eingebauten Zustand der Klappenvorrichtung im geodätisch unten liegenden Bereich der Lageraufnahme ausgebildet ist. Dies bedeutet, dass aufgrund der Schwerkraft vorhandene Flüssigkeiten auch in geringen Mengen immer zur Bohrung gelangen, da diese am tiefsten Punkt der Lageraufnahme ausgebildet ist. It is particularly advantageous if the bore is formed in the installed state of the flap device in the geodetically underlying area of the bearing receptacle. This means that due to gravity existing liquids always get to the hole even in small quantities, since this is formed at the lowest point of the bearing support.
Des Weiteren ist die Bohrung in der den Strömungskanal verschließenden Stellung des Klappenkörpers vorzugsweise an der stromabwärtigen Seite des Klappenkörpers angeordnet. Bei angestelltem Klappenkörper im Strömungskanal entsteht durch diese Anordnung eine Druckdifferenz zwischen dem Raum zwischen den beiden Lagern und dem Ende der Bohrung im Strömungskanal. So wird sichergestellt, dass bei Teillast in den Bereich des Lagers eintretende Flüssigkeiten vollständig wieder über die Bohrung abgeführt werden. Auch eindringende heiße Gase werden über die Bohrung abgesaugt, wodurch die thermische Belastbarkeit des Aktors erhöht wird. Furthermore, the bore in the flow passage closing position of the flap body is preferably arranged on the downstream side of the flap body. When the valve body in the flow channel is established by this arrangement creates a pressure difference between the space between the two bearings and the end of the bore in the flow channel. This ensures that at partial load in the area of the bearing entering fluids are completely dissipated again over the hole. Penetrating hot gases are also sucked out through the bore, which increases the thermal load capacity of the actuator.
Vorzugsweise ist das zweite Lager beabstandet zum ersten Lager in einer Lageraufnahme des Aktorgehäuses angeordnet. So wird eine zuverlässige leicht drehbare Lagerung der Welle sichergestellt. Der Raum zur Aufnahme des Kondenswassers bildet sich somit zwischen den beiden Gehäusen, wodurch die Herstellung der Bohrung deutlich vereinfacht wird. Preferably, the second bearing is arranged at a distance from the first bearing in a bearing receptacle of the actuator housing. This ensures a reliable, easily rotatable bearing of the shaft. The space for receiving the condensate water thus forms between the two housings, whereby the production of the bore is significantly simplified.
In einer besonders bevorzugten Ausführungsform verläuft der Strömungskanal waagerecht und die Bohrung ist in einer Ebene angeordnet, die durch einen Vektor, der senkrecht zur Mittelachse des Strömungskanals und einen Vektor, der entlang der Wellenachse verläuft, aufgespannt ist. Auf diese Weise kann die Bohrung auch bei waagerecht verlaufendem Strömungskanal an der tiefsten Stelle angeordnet werden, wodurch der Ablauft des Wassers und von Verunreinigungen sichergestellt wird. In a particularly preferred embodiment, the flow channel runs horizontally and the bore is arranged in a plane which is defined by a vector which is perpendicular to the central axis of the flow channel and a vector which runs along the shaft axis. is stretched. In this way, the bore can also be arranged at horizontally extending flow channel at the lowest point, whereby the runoff of the water and impurities is ensured.
In einer hierzu weiterführenden Ausgestaltung ist der Klappenkörper derart sphärisch geformt, dass die Bohrung in allen Positionen des Klappenkörpers frei durchströmbar ist und im geschlossenen Zustand an deren stromabwärtigen Seite angeordnet ist. Die freie Durchströmbarkeit der Bohrung ermöglicht bei Teillast die Nutzung der Druckdifferenz an der Rückseite des geschlossenen Klappenkörpers im Vergleich zum Raum zwischen den beiden Lagern, während bei Volllast aufgrund nicht vorhandener Druckdifferenzen nicht mit einem Eindringen von Flüssigkeiten oder heißen blow-by Gasen in den Raum zu rechnen ist. In a further refinement of this, the flap body is of such spherical shape that the bore can be freely flowed through in all positions of the flap body and is arranged in the closed state on its downstream side. The free flow of the bore allows at partial load, the use of the pressure difference at the back of the closed valve body compared to the space between the two camps, while at full load due to lack of pressure differences not with the ingress of liquids or hot blow-by gases in the room is calculated.
Es wird somit eine Klappenvorrichtung für eine Verbrennungskraftmaschine geschaffen, mit der ein zuverlässiger Ablauf von Flüssigkeiten, die entlang der Welle hinter das erste Lager gelangen, in den Strömungskanal sichergestellt wird. Dies erhöht die Lebensdauer der Lager und verhindert ein Einfrieren und somit Steckenbleiben der Welle. Gleichzeitig werden auch thermische Vorteile erzielt, da heiße Abgase zurück in den Kanal und nicht in Richtung des Aktors geleitet werden. It is thus provided a flap device for an internal combustion engine, with the reliable flow of liquids, which pass along the shaft behind the first bearing, is ensured in the flow channel. This increases the life of the bearings and prevents freezing and thus sticking of the shaft. At the same time thermal benefits are achieved because hot exhaust gases are routed back into the channel and not in the direction of the actuator.
Ein Ausführungsbeispiel einer erfindungsgemäßen Klappenvorrichtung ist in den Figuren dargestellt und wird nachfolgend beschrieben. An embodiment of a flap device according to the invention is shown in the figures and will be described below.
Figur 1 zeigt eine Seitenansicht einer erfindungsgemäßen Klappenvorrichtung in geschnittener Darstellung. Figur 2 zeigt eine perspektivische Ansicht eines Strömungskanals der Klappenvorrichtung gemäß der Figur 1, der in Höhe der Welle geschnitten dargestellt ist. Figure 1 shows a side view of a flap device according to the invention in a sectional view. Figure 2 shows a perspective view of a flow channel of the flap device according to the figure 1, which is shown cut at the level of the shaft.
Die erfindungsgemäße Klappenvorrichtung weist ein Strömungsgehäuse 10 auf, welches einen Strömungskanal 12 begrenzt. Im Strömungskanal 12 ist ein Klappenkörper 14 angeordnet, über den der Durchströmungsquerschnitt des Strömungskanals 12 geregelt werden kann, indem der Klappenkörper 14 im Strömungskanal 12 gedreht wird.  The flap device according to the invention has a flow housing 10 which delimits a flow channel 12. In the flow channel 12, a flap body 14 is arranged, via which the flow cross-section of the flow channel 12 can be controlled by the flap body 14 is rotated in the flow channel 12.
Hierzu ist der Klappenkörper 14 auf einer Welle 16 befestigt, die durch das Strömungsgehäuse 10 in den Strömungskanal 12 ragt. Am zum Klappenkörper 14 gegenüberliegenden Ende ist auf der Welle 16 ein Abtriebszahnrad 18 befestigt, welches Teil eines als Stirnradgetriebe ausgebildeten Getriebes 20 ist. Dieses Getriebe 20 wird über einen Elektromotor 22 bei entsprechender Bestromung des Elektromotors 22 angetrieben. Hierzu ist auf einer Ausgangswelle 24 des Elektromotors 22 ein Antriebsritzel 26 befestigt, welches als Antriebsglied des Getriebes 20 wirkt, so dass die Drehbewegung des Elektromotors 22 untersetzt über das Getriebe 20 auf die Welle 16 und damit auf den Klappenkörper 14 übertragen wird. For this purpose, the flap body 14 is mounted on a shaft 16 which projects through the flow housing 10 into the flow channel 12. At the opposite end of the valve body 14, a driven gear 18 is mounted on the shaft 16, which is part of a transmission 20 designed as a spur gear. This transmission 20 is driven by an electric motor 22 with appropriate energization of the electric motor 22. For this purpose, a drive pinion 26 is mounted on an output shaft 24 of the electric motor 22, which acts as a drive member of the transmission 20, so that the rotational movement of the electric motor 22 is transmitted via the gear 20 geared to the shaft 16 and thus to the valve body 14.
Der Elektromotor 22 und das Getriebe 20 dienen somit als Aktor 28 der Klappenvorrichtung und sind in einem gemeinsamen Aktorgehäuse 30 angeordnet, welches aus einem Hauptgehäuseteil 32, in dem der Elektromotor 22 sowie das Getriebe 20 montiert sind und einem einen Aktorinnenraum 34 verschließenden Deckel 36 besteht, der unter Zwischenlage einer Dichtung 38 am Hauptgehäuseteil 32 befestigt ist. Um den verwendeten Bauraum möglichst gering zu halten und den Elektromotor sowie das Getriebe 20 im Hauptgehäuseteil 32 einfach montieren zu können, ragt der parallel zur Welle 16 angeordnete Elektromotor 22 parallel zur Welle 16 in Richtung des Strömungsgehäuses 10. Am Strömungsgehäuse 10 ist eine Lageraufnahme 40 in Form eines hohlzylindrischen Vorsprungs 42 ausgebildet, der sich in Richtung eines hohlzylindrischen Aufnahmeelementes 44 am Aktorgehäuse 30 erstreckt. Das Innere dieses hohlzylindrischen Aufnahmeelementes 44 bildet eine radial begrenzte Aufnahmeöffnung 46, in die der hohlzylindrische Vorsprung 42 des Strömungsgehäuses 10 ragt, wobei der Innendurchmesser der Aufnahmeöffnung 46 im Wesentlichen dem Außendurchmesser des Aufnahmeelementes 44 entspricht. Bei der Montage wird das axiale Ende des hohlzylindrischen Vorsprungs 42 gegen ein absatzförmige Ende 48 der Aufnahmeöffnung 46 unter Zwischenlage einer Axialdichtung 50 geschoben. The electric motor 22 and the gear 20 thus serve as an actuator 28 of the flap device and are arranged in a common actuator housing 30, which consists of a main housing part 32, in which the electric motor 22 and the gear 20 are mounted and an actuator interior 34 occlusive cover 36, which is fastened with the interposition of a seal 38 on the main housing part 32. In order to keep the space used as small as possible and to be able to easily assemble the electric motor and the gear 20 in the main housing part 32, the electric motor 22 arranged parallel to the shaft 16 projects parallel to the shaft 16 in the direction of the flow housing 10. At the flow housing 10, a bearing receptacle 40 in the form of a hollow cylindrical projection 42 is formed, which extends in the direction of a hollow cylindrical receiving element 44 on the actuator housing 30. The interior of this hollow cylindrical receiving element 44 forms a radially limited receiving opening 46, in which the hollow cylindrical projection 42 of the flow housing 10 projects, wherein the inner diameter of the receiving opening 46 substantially corresponds to the outer diameter of the receiving element 44. During assembly, the axial end of the hollow cylindrical projection 42 is pushed against a shoulder-shaped end 48 of the receiving opening 46 with the interposition of an axial seal 50.
An das Aufnahmeelement 44 schließt sich in den Aktorinnenraum 34 ragend ein hohlzylindrischer Vorsprung 52 verkleinerten Durchmessers an, so dass zwischen dem sich axial erstreckenden Aufnahmeelement 44 und dem sich axial erstreckenden hohlzylindrischen Vorsprung 52 ein weiterer Absatz 54 ausgebildet ist. Der zweite hohlzylindrische Vorsprung 52 des Aktorgehäuses 30 dient als zweite Lageraufnahme 56. Adjoining the receiving element 44 in the actuator interior 34 projecting a hollow cylindrical projection 52 of reduced diameter, so that between the axially extending receiving element 44 and the axially extending hollow cylindrical projection 52, a further shoulder 54 is formed. The second hollow-cylindrical projection 52 of the actuator housing 30 serves as a second bearing receptacle 56.
In der ersten Lageraufnahme 40 des Strömungsgehäuses 10 ist ein als Gleitlager ausgeführtes erstes Lager 58 für die Welle 16 angeordnet, welches aus Kohle-Graphit hergestellt ist und axial gegen eine die Wellendurchführungsöffnung radial begrenzende Wand 57 anliegt. Die Welle 16 erstreckt sich durch das erste Lager 58 und über den in den Aktorinnenraum 34 ragenden Vorsprung 52 hinaus in den Aktorinnenraum 34. Die zweite Lageraufnahme 56 weist eine Querschnittsverengung auf, an deren entgegengesetzten Enden jeweils ein Absatz 60, 62 gebildet wird. Die Vorsprünge 42, 52, das Aufnahmeelement 44 sowie die Lager weisen eine gemeinsame Mittelachse 63 auf, die gleichzeitig die Wellenachse ist. Radial innerhalb dieses verengten Querschnitts ist ein zweites Lager 64 angeordnet, welches ebenfalls als Kohle-Graphit-Gleitlager ausgeführt ist, so dass die Welle 16 zweifach an einer Klappenseite gelagert ist. Das zum Klappenkörper 14 weisende axiale Ende dieses Lagers 64 ragt geringfügig über den Absatz 54 hinaus. Auf diese Weise wird es möglich, dass eine fest auf der Welle 16 angeordnete Anlaufscheibe 66 über eine Dreh- und Druckfeder 68 zur axialen Lagefixierung der Welle 16 gegen das zweite Lager 64 gedrückt wird. In the first bearing seat 40 of the flow housing 10 designed as a plain bearing first bearing 58 is arranged for the shaft 16, which is made of carbon-graphite and axially abuts against the shaft passage opening radially bounding wall 57. The shaft 16 extends through the first bearing 58 and beyond the projection 52 projecting into the actuator interior 34 into the actuator interior 34. The second bearing receiver 56 has a cross-sectional constriction, at the opposite ends of which a shoulder 60, 62 is formed. The projections 42, 52, the receiving element 44 and the bearings have a common center axis 63, which is also the shaft axis. Radially within this narrowed cross section, a second bearing 64 is arranged, which is also designed as a carbon graphite sliding bearing, so that the shaft 16 is mounted twice on a flap side. The valve body 14 facing axial end of this bearing 64 protrudes slightly beyond the heel 54 addition. In this way, it is possible that a thrust washer 66 fixedly arranged on the shaft 16 is pressed against the second bearing 64 via a rotary and compression spring 68 for axial positional fixing of the shaft 16.
Diese Dreh-Druckfeder 68 ist im Aktorinnenraum 34, den Vorsprung 52 radial umgebend angeordnet und drückt gegen das fest auf der Welle 16 angeordnete Abtriebszahnrad 18, so dass mit diesem auch die Welle 16 in dieser axialen Richtung belastet wird. Des Weiteren greifen die beiden Endschenkel der Feder 68 in bekannter Weise derart hinter in der Figur 1 nicht erkennbare Vorsprünge am Aktorgehäuse 30 und am Abtriebszahnrad 18, dass die Welle 16 in eine Richtung zumindest bei Drehung aus der Ruhestellung vorgespannt ist. Entsprechend wird die Welle 16 aufgrund der Federkraft bei Ausfall des Elektromotors 22 in eine Notlaufposition gedreht. This rotary compression spring 68 is arranged in the actuator interior 34, the projection 52 radially surrounding and presses against the fixedly arranged on the shaft 16 driven gear 18, so that with this, the shaft 16 is loaded in this axial direction. Furthermore, the two end legs of the spring 68 engage in a known manner so behind behind in Figure 1 unrecognizable projections on the actuator housing 30 and the output gear 18 that the shaft 16 is biased in one direction at least during rotation from the rest position. Accordingly, the shaft 16 is rotated due to the spring force in case of failure of the electric motor 22 in a Notlaufposition.
Am in den Aktorinnenraum weisenden Ende des Vorsprungs 52 ist die Welle 16 umgebend ein Dichtring 70 angeordnet, der axial gegen den Absatz 62 anliegt und die Wellendurchführung durch die Lageraufnahme 56 in Richtung des Aktorinnenraums 34 abdichtet. At the end of the projection 52 pointing in the actuator interior, the shaft 16 is surrounded by a sealing ring 70, which abuts axially against the shoulder 62 and seals the shaft passage through the bearing receptacle 56 in the direction of the actuator interior 34.
Die Befestigung des Strömungsgehäuses am Aktorgehäuse 30 erfolgt über Verbindungsplatten 72, die beispielsweise durch Schweißen am Strömungsgehäuse 10 befestigt sind und an denen über Schrauben 73 das Aktorgehäuse 30 befestigt ist. The attachment of the flow housing on the actuator housing 30 via connecting plates 72, which are attached for example by welding to the flow housing 10 and to which the actuator housing 30 is attached by screws 73.
Im Betrieb, also bei laufendem Verbrennungsmotor, wird der Strömungskanal 10 von Abgas durchströmt. Dieses Abgas beinhaltet Wasser und andere Verunreinigungen. Beides dringt durch die Pulsationen im Abgasstrang entlang der Welle 16 in einen Raum 74 zwischen den beiden Lagern 58, 64 und kann dort insbesondere nach dem Abschalten des Verbrennungsmotors kondensieren. Bei Temperaturen unter 0°C führt dies zu einer Eisbildung im Bereich des Lagers 58, was wiederum zu Schäden am Lager 58 oder einem Steckenbleiben der Welle 16 führen kann. During operation, ie when the internal combustion engine is running, the flow channel 10 is flowed through by exhaust gas. This exhaust gas includes Water and other impurities. Both penetrate through the pulsations in the exhaust line along the shaft 16 in a space 74 between the two bearings 58, 64 and can condense there in particular after switching off the internal combustion engine. At temperatures below 0 ° C, this leads to ice formation in the area of the bearing 58, which in turn can lead to damage to the bearing 58 or sticking of the shaft 16.
Um dies zu vermeiden, ist am hohlzylindrischen Vorsprung 42 eine Bohrung 76 ausgebildet, die sich vom Raum 74 in den Strömungskanal 12 erstreckt und parallel zur Welle 16 verläuft. Um diese Bohrung 76 besonders einfach herstellen zu können, erweitert sich die Lageraufnahme 40 in Form einer absatzförmigen Erweiterung 78 in Richtung des Aktorgehäuses 30. Diese absatzförmige Erweiterung 78 ist in Höhe eines axialen Endes 82 des ersten Lagers 58 ausgebildet, so dass sich kein Wasser innerhalb des Vorsprungs 42 auf dem Lager 58 befinden kann, wenn der Einbau der Klappenvorrichtung im Abgasstrang der Verbrennungskraftmaschine so erfolgt, dass der Anfang dieser Bohrung 76 an der geodätisch niedrigsten Position des Raumes 74 angeordnet ist und die Bohrung 76 in Richtung zum Strömungskanal 12 stetig abfällt, so dass Kondenswasser aus dem Raum 74 aufgrund der Gravitation immer in Richtung der Bohrung 76 und durch diese hindurch in Richtung des Strömungskanals 12 strömt. Um zusätzlich ein Strömen in dieser Richtung auch bei warmem Verbrennungsmotor, also während des Betriebes, sicher zu stellen, befindet sich die Bohrung 76 an der stromabwärtigen Seite des Klappenkörpers 14 im geschlossenen Zustand des Klappenkörpers 14, da an dieser Seite im Betrieb bei Teillast, also geschlossenem Klappenkörper 14 ein Unterdruck entsteht, der eine Saugwirkung gegenüber dem Raum 74 erzeugt. To avoid this, a bore 76 is formed on the hollow cylindrical projection 42 which extends from the space 74 into the flow channel 12 and extends parallel to the shaft 16. In order to be able to produce this bore 76 in a particularly simple manner, the bearing receptacle 40 widens in the form of a shoulder-shaped enlargement 78 in the direction of the actuator housing 30. This shoulder-shaped enlargement 78 is formed at the level of an axial end 82 of the first bearing 58, so that there is no water inside the protrusion 42 may be located on the bearing 58, when the installation of the flap device in the exhaust line of the internal combustion engine is such that the beginning of this bore 76 is disposed at the geodetically lowest position of the space 74 and the bore 76 steadily drops in the direction of the flow channel 12, so that condensation from the space 74 always flows in the direction of the bore 76 and through it in the direction of the flow channel 12 due to gravity. In order to additionally ensure flow in this direction, even when the internal combustion engine is warm, that is to say during operation, the bore 76 is located on the downstream side of the valve body 14 in the closed state of the valve body 14, since at this part in operation at part load, ie closed valve body 14 creates a negative pressure, which creates a suction against the space 74.
Da gleichzeitig der Einbau dieser Klappenvorrichtung zumeist an einem waagerechten Strömungskanal 12 stattfindet, sind diese beiden Bedingungen dadurch zu erreichen, dass die Bohrung 76 in einer Ebene angeordnet ist, die durch einen Vektor, der senkrecht zur Mittelachse des Strömungskanals 12 und einen Vektor, der entlang der Wellenachse verläuft, aufgespannt ist. Zusätzlich ist der Klappenkörper 14 in der Weise sphärisch geformt, dass er eine Wölbung 80 aufweist, die derart angeordnet ist, dass der Außenumfang des Klappenkörpers 14 zur stromaufwärtigen Seite geneigt ist. Since at the same time the installation of this flap device usually takes place on a horizontal flow channel 12, these two Conditions are achieved in that the bore 76 is arranged in a plane which is spanned by a vector which is perpendicular to the central axis of the flow channel 12 and a vector which is along the shaft axis. In addition, the door body 14 is spherically shaped to have a bulge 80 arranged such that the outer periphery of the door body 14 is inclined to the upstream side.
Bei Volllast befindet sich der Klappenkörper 14 in seiner den Strömungskanal 12 öffnenden Stellung, in der jedoch lediglich geringe Druckdifferenzen auftreten, so dass der Eintrag an Abgas entlang der Welle 16 in den Raum 74 lediglich gering ist und hohe Abgastemperaturen vorliegen, die ein Kondensieren des Wassers im Abgas verhindern. At full load, the flap body 14 is in its position opening the flow channel 12, in which, however, only small pressure differences occur, so that the entry of exhaust gas along the shaft 16 in the space 74 is only low and high exhaust gas temperatures are present, which is a condensation of the water prevent in the exhaust.
Durch den Raum 74 zwischen den beiden Lagern 58, 64 werden Druckdifferenzen, die dazu führen, dass Abgas entlang der Welle 16 bis an das Innere des Aktors 28 strömt, vermieden, da ein Druckabbau über den Raum 74 stattfindet. Through the space 74 between the two bearings 58, 64 pressure differences, which cause exhaust gas along the shaft 16 to flow to the interior of the actuator 28, avoided as a pressure reduction takes place via the space 74.
Es wird somit eine Klappenvorrichtung geschaffen, bei der Schäden des Aktors oder ein Steckenbleiben der Welle durch gefrierendes Wasser oder andere Verunreinigungen vermieden werden. Gleichzeitig wird im Betrieb des Verbrennungsmotors dem Raum zwischen den Lagern Wärme entzogen, da das Abgas aus dem Raum in Richtung des Strömungskanals gesaugt wird. Trotz der direkten Anbindung der Klappenwelle in den Aktorinnenraum wird der Aktor nicht thermisch überlastet, da kein heißes Abgas aufgrund von Druckdifferenzen in das Innere des Aktors eindringt. There is thus provided a flap device in which damage to the actuator or sticking of the shaft by freezing water or other contaminants are avoided. At the same time, the space between the bearings heat is removed during operation of the internal combustion engine, since the exhaust gas is sucked out of the room in the direction of the flow channel. Despite the direct connection of the valve shaft in the actuator interior, the actuator is not thermally overloaded because no hot exhaust gas penetrates due to pressure differences in the interior of the actuator.
Es sollte deutlich sein, dass der Schutzbereich des vorliegenden Hauptanspruchs nicht auf das beschriebene Ausführungsbeispiel begrenzt ist. Insbesondere können die konstruktive Ausgestaltung der Gehäuse, die verwendeten Antriebe oder Getriebe sowie die Kanal und Klappenformen abgeändert werden. Auch können unterschiedliche Lager und Dichtungen verwendet werden. Auch kann die Bohrung je nach Ausführung des Lagers am Lager selbst ausgebildet werden. It should be understood that the scope of the present invention is not limited to the embodiment described. In particular, the structural design of the housing, the drives or gearbox used as well as the channel and flap shapes are modified. Also, different bearings and seals can be used. Also, the hole can be formed depending on the design of the bearing on the camp itself.

Claims

P A T E N T A N S P R Ü C H E P A T E N T A N S P R E C H E
Klappenvorrichtung für eine Verbrennungskraftmaschine mit einem Strömungsgehäuse (10), das einen Strömungskanal (12) begrenzt, Flap device for an internal combustion engine with a flow housing (10) which delimits a flow channel (12),
einem Klappenkörper (14), der drehbar im Strömungskanal (12) angeordnet ist, a flap body (14) which is rotatably arranged in the flow channel (12),
einer einseitig gelagerten Welle (16), auf der der Klappenkörper (14) befestigt ist, a unilaterally mounted shaft (16) on which the flap body (14) is fixed,
einem ersten Lager (58), das in einer ersten Lageraufnahme (40) angeordnet ist und die Welle (16) radial umgibt, a first bearing (58) disposed in a first bearing receptacle (40) and radially surrounding the shaft (16),
einem Aktor (28), über den die Welle (16) und der Klappenkörper (14) im Strömungskanal (12) drehbar sind, an actuator (28), via which the shaft (16) and the flap body (14) are rotatable in the flow channel (12),
einem Aktorgehäuse (30), in dem der Aktor (28) angeordnet ist und einer Bohrung (76), die von einem die Welle (16) umgebenden Raum (74) in den Strömungskanal (12) mündet, an actuator housing (30) in which the actuator (28) is arranged and a bore (76) which opens into the flow channel (12) from a space (74) surrounding the shaft (16),
dadurch gekennzeichnet, dass characterized in that
die Welle (16) in das Aktorgehäuse (30) ragt und über das erste Lager (58) und ein zweites Lager (64) einseitig gelagert ist, the shaft (16) protrudes into the actuator housing (30) and is mounted on one side via the first bearing (58) and a second bearing (64),
wobei die erste Lageraufnahme (40) am Strömungsgehäuse (10) ausgebildet ist und der Raum (74), von dem aus die Bohrung (76) in den Strömungskanal (12) mündet, zwischen dem ersten Lager (58) und dem zweiten Lager (64) angeordnet ist. wherein the first bearing receptacle (40) is formed on the flow housing (10) and the space (74) from which the bore (76) opens into the flow channel (12), between the first bearing (58) and the second bearing (64 ) is arranged.
Klappenvorrichtung für eine Verbrennungskraftmaschine nach Anspruch 1, Flap device for an internal combustion engine according to claim 1,
dadurch gekennzeichnet, dass characterized in that
die Bohrung (76) in der ersten Lageraufnahme (40) ausgebildet ist, welche am Strömungsgehäuse (10) ausgebildet ist. the bore (76) is formed in the first bearing receptacle (40) which is formed on the flow housing (10).
3. Klappenvorrichtung für eine Verbrennungskraftmaschine nach Anspruch 1, 3. damper device for an internal combustion engine according to claim 1,
dadurch gekennzeichnet, dass  characterized in that
die Bohrung (76) im ersten Lager (58) ausgebildet ist.  the bore (76) is formed in the first bearing (58).
4. Klappenvorrichtung für eine Verbrennungskraftmaschine nach Anspruch 2, 4. flap device for an internal combustion engine according to claim 2,
dadurch gekennzeichnet, dass  characterized in that
am axialen Ende (82) des ersten Lagers (58) an der zum Strömungskanal (12) entgegengesetzten Seite der Lageraufnahme (58) eine absatzförmige Erweiterung (78) ausgebildet ist und die Bohrung (76) sich parallel zur Welle (16) von der absatzförmigen Erweiterung (78) aus in den Strömungskanal (12) erstreckt.  at the axial end (82) of the first bearing (58) on the flow channel (12) opposite side of the bearing receptacle (58) is a shoulder-shaped extension (78) is formed and the bore (76) parallel to the shaft (16) of the heel-shaped Extension (78) extends out into the flow channel (12).
5. Klappenvorrichtung für eine Verbrennungskraftmaschine nach einem der Ansprüche 2 bis 4, 5. damper device for an internal combustion engine according to one of claims 2 to 4,
dadurch gekennzeichnet, dass  characterized in that
die Bohrung (76) im eingebauten Zustand der Klappenvorrichtung im geodätisch unten liegenden Bereich der ersten Lageraufnahme (40) oder des ersten Lagers (58) ausgebildet ist.  the bore (76) is formed in the installed state of the flap device in the geodetically lower region of the first bearing receptacle (40) or of the first bearing (58).
6. Klappenvorrichtung für eine Verbrennungskraftmaschine nach einem der vorhergehenden Ansprüche, 6. flap device for an internal combustion engine according to any one of the preceding claims,
dadurch gekennzeichnet, dass  characterized in that
die Bohrung (76) in der den Strömungskanal (12) verschließenden Stellung des Klappenkörpers (14) an der stromabwärtigen Seite des Klappenkörpers (14) angeordnet ist.  the bore (76) in the flow channel (12) closing position of the flap body (14) on the downstream side of the flap body (14) is arranged.
7. Klappenvorrichtung für eine Verbrennungskraftmaschine nach einem der vorhergehenden Ansprüche, 7. damper device for an internal combustion engine according to any one of the preceding claims,
dadurch gekennzeichnet, dass das zweite Lager (64) beabstandet zum ersten Lager (58) in einer Lageraufnahme (56) des Aktorgehäuses (30) angeordnet ist. characterized in that the second bearing (64) spaced from the first bearing (58) in a bearing receptacle (56) of the actuator housing (30) is arranged.
8. Klappenvorrichtung für eine Verbrennungskraftmaschine nach einem der vorhergehenden Ansprüche, 8. flap device for an internal combustion engine according to any one of the preceding claims,
dadurch gekennzeichnet, dass  characterized in that
der Strömungskanal (12) waagerecht verläuft und die Bohrung (76) in einer Ebene angeordnet ist, die durch einen Vektor, der senkrecht zur Mittelachse des Strömungskanals (12) und einen Vektor, der entlang der Wellenachse verläuft, aufgespannt ist.  the flow channel (12) is horizontal and the bore (76) is disposed in a plane defined by a vector perpendicular to the central axis of the flow channel (12) and a vector extending along the shaft axis.
9. Klappenvorrichtung für eine Verbrennungskraftmaschine nach einem der vorhergehenden Ansprüche, 9. damper device for an internal combustion engine according to any one of the preceding claims,
dadurch gekennzeichnet, dass  characterized in that
der Klappenkörper (14) derart sphärisch geformt ist, dass die Bohrung (76) in allen Positionen des Klappenkörpers (14) frei durchströmbar ist und im geschlossenen Zustand an deren stromabwärtigen Seite angeordnet ist.  the flap body (14) is spherically shaped in such a way that the bore (76) can be flowed through freely in all positions of the flap body (14) and is arranged in its closed state on its downstream side.
EP15707573.0A 2014-04-01 2015-02-19 Flap device for an internal combustion engine Active EP3126651B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014104579.3A DE102014104579B4 (en) 2014-04-01 2014-04-01 Valve device for an internal combustion engine
PCT/EP2015/053472 WO2015149989A1 (en) 2014-04-01 2015-02-19 Flap device for an internal combustion engine

Publications (2)

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EP3126651A1 true EP3126651A1 (en) 2017-02-08
EP3126651B1 EP3126651B1 (en) 2017-12-27

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EP15707573.0A Active EP3126651B1 (en) 2014-04-01 2015-02-19 Flap device for an internal combustion engine

Country Status (4)

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US (1) US10145310B2 (en)
EP (1) EP3126651B1 (en)
DE (1) DE102014104579B4 (en)
WO (1) WO2015149989A1 (en)

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Also Published As

Publication number Publication date
EP3126651B1 (en) 2017-12-27
US20170030269A1 (en) 2017-02-02
DE102014104579B4 (en) 2017-05-11
DE102014104579A1 (en) 2015-10-01
US10145310B2 (en) 2018-12-04
WO2015149989A1 (en) 2015-10-08

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